EP2415563A1 - Impact tool - Google Patents
Impact tool Download PDFInfo
- Publication number
- EP2415563A1 EP2415563A1 EP10758826A EP10758826A EP2415563A1 EP 2415563 A1 EP2415563 A1 EP 2415563A1 EP 10758826 A EP10758826 A EP 10758826A EP 10758826 A EP10758826 A EP 10758826A EP 2415563 A1 EP2415563 A1 EP 2415563A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- outer housing
- gear
- impact
- axial direction
- tool
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D17/00—Details of, or accessories for, portable power-driven percussive tools
- B25D17/24—Damping the reaction force
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
- B25D16/006—Mode changers; Mechanisms connected thereto
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D17/00—Details of, or accessories for, portable power-driven percussive tools
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
- B25D2211/003—Crossed drill and motor spindles
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
- B25D2211/06—Means for driving the impulse member
- B25D2211/068—Crank-actuated impulse-driving mechanisms
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2222/00—Materials of the tool or the workpiece
- B25D2222/54—Plastics
- B25D2222/57—Elastomers, e.g. rubber
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
- B25D2250/085—Elastic behaviour of tool components
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
- B25D2250/245—Spatial arrangement of components of the tool relative to each other
Definitions
- the hammer bit 119 is held by the hollow tool holder 137 such that it is allowed to linearly move with respect to the tool holder in its axial direction.
- the outer housing 103, the hammer bit 119 and the handgrip 109 are features that correspond to the "outer housing", the "tool bit” and the "handle”, respectively, according to the present invention.
- the side of the hammer bit 119 is taken as the front and the side of the handgrip 109 as the rear.
- the torque transmitted to the intermediate shaft 145 is then transmitted from the first bevel gear 147 that rotates together with the intermediate shaft 145 in a horizontal plane, to the second bevel gear 149 that rotates in a vertical plane in engagement with the first bevel gear 147, and then further transmitted from the second bevel gear 149 to the rotary sleeve 151.
- the striker 133 is caused to linearly move within the cylinder 131 via air pressure fluctuations or air spring action in the air chamber 131a of the cylinder 131.
- the striker 133 then collides with the impact bolt 135, so that the kinetic energy caused by this collision is transmitted to the hammer bit 119.
- the third and fourth bevel gears 153, 155 supported via the bearings 167, 169 in the bearing cover 163 are connected such that they can move together with the motion converting mechanism 113 in the axial direction of the hammer bit with respect to the outer housing 103. Therefore, the positional relation between the motion converting mechanism 113 and the third and fourth bevel gears 153, 155 is held constant regardless of vibration, so that stable and smooth movement can be ensured.
- an outer housing 203 is integrally formed with a handgrip 209.
- the outer housing 203 and the handgrip 209 are features that correspond to the "outer housing" and the "handle", respectively, according to the present invention.
- the outer housing 203 houses a motor housing 208 which houses a driving motor 211, and an inner housing 205 which houses the motion converting mechanism 213, the striking mechanism and the power transmitting mechanism 217.
- the driving motor 211 is driven when a user depresses a trigger 209a disposed on the handgrip 209.
- the driving motor 211 is disposed such that its rotation axis runs in a vertical direction (vertically as viewed in FIG.
- the mass of the handgrip 209 which is integrated with the outer housing 203 can be made relatively large with respect to the inner housing 205 which houses the striking mechanism part, so that the effect of vibration-proofing the handgrip 109 can be enhanced.
- the elastic rubbers 283 284 are described as being spherical, but they may be cylindrical.
- the joint structure of the split output shaft 212 is described as being constructed such that the hexagonal hole 291 is formed in the body-side shaft part 212a and the spherical element 292 having a hexagonal section is formed in the tip-side shaft part 212b, but they may be formed vice versa.
- the universal joint is not limited to the structure comprising the hexagonal hole 291 and the spherical element 292 having a hexagonal section.
Abstract
Description
- The present invention relates to a technique for vibration-proofing an impact tool in which a tool bit is caused to perform a predetermined hammering operation by linearly moving in its axial direction.
- Japanese laid-open Patent Publication No.
2003-39344 - In this electric hammer, transmission of vibration from the striking mechanism unit to the handle can be reduced by the elastic member, but a further improvement is desired in the effect of vibration-proofing the handle.
- Accordingly, it is an object of the present invention to further improve the effect of vibration-proofing a handle in an impact tool.
- In order to solve the above-described problem, according to a preferred embodiment of the present invention, an impact tool is provided with a tool bit which is caused to linearly move in an axial direction of the tool bit and thereby perform a predetermined operation. The "impact tool" in this invention suitably includes a hammer in which a tool bit is caused to linearly move in the axial direction, and a hammer drill in which a tool bit is caused to linearly move in the axial direction and rotate around its axis.
The impact tool according to this invention is characterized in that it includes a handle to be held by a user, an outer housing that is integrally formed with the handle, a motor that is disposed in an outer housing such that its rotation axis runs transversely to the axial direction of the tool bit, a gear that is rotationally driven by receiving torque of the motor in the outer housing, an impact driving part that is driven by the gear in the outer housing, and a striking element that is driven by the impact driving part and linearly moves the tool bit. Further, the motor is mounted to the outer housing, and the outer housing is connected to the impact driving part and the gear via an elastic element and can move in the axial direction of the tool bit with respect to the impact driving part and the gear. - According to this invention, the outer housing integrally formed with the handle is connected via the elastic element to the impact driving part and the gear which are sources of vibration such that it can move in the axial direction of the tool bit with respect to the impact driving part and the gear, and the motor is mounted to the outer housing. With such a construction in which the motor as a mass is mounted to the outer housing, the mass of the handle which is integrated with the outer housing can be made relatively large with respect to the impact driving part, so that the effect of vibration-proofing the handle can be enhanced. Particularly, in this invention, the outer housing is connected via the elastic element such that it can move with respect to the impact driving part and the gear in the axial direction of the tool bit. With this construction, the positional relation between the impact driving part and the gear which drives the impact driving part is held constant, so that stable and smooth movement can be ensured.
- According to a further embodiment of the impact tool of the present invention, the motor is fixed to the outer housing and integrated with the handle. With such a construction, integration of the motor with the handle can be further enhanced.
- According to a further embodiment of the impact tool of the present invention, the impact tool includes a torque transmitting member that is disposed on the outer housing side and rotates around an axis of the tool bit by receiving torque of the motor, and a power transmitting gear that rotates together with the torque transmitting member and transmits the torque to the gear. Further, the power transmitting gear can move together with the impact driving part in the axial direction of the tool bit with respect to the torque transmitting member while being held in engagement with the gear. The "torque transmitting member" in this invention typically comprises a cylindrical member, and it suitably includes a cylindrical member having an opening such as a slit or a hole in its circumferential surface.
According to this invention having the above-described construction, when the impact driving part and the outer housing move in the axial direction of the hammer bit with respect to each other due to vibration caused by driving of the impact driving part and the striking element, the torque transmitting member and the power transmitting gear correspondingly move with respect to each other. Thus, via the torque transmitting member and the power transmitting gear, torque can be transmitted from the motor to the gear with stability. - According to a further embodiment of the impact tool of the present invention, the impact tool further includes a bit driving gear that causes the tool bit to rotate in a circumferential direction by receiving the torque of the motor. Further, the power transmitting gear is rotationally driven by the bit driving gear via the torque transmitting member. According to this invention, with such a construction, the impact driving part can be driven by power obtained from a rotary drive path of the tool bit.
- According to a further embodiment of the impact tool of the present invention, an end of the motor which faces away from an axis of the tool bit in a direction of a rotation axis of the motor is mounted to the outer housing such that the motor can rotate in the axial direction of the tool bit.
According to this invention, by rotatably mounting the motor to the outer housing, the motor can be utilized as a mass of the handle, so that transmissibility of vibration from the impact driving part which is a source of vibration to the handle can be reduced. With such a construction, when the outer housing and the impact driving part move with respect to each other in the axial direction of the tool bit due to vibration, the impact tool can respond to such movement, while improving the effect of vibration-proofing the handle with respect to the impact driving part. - According to a further embodiment of the impact tool of the present invention, in the construction in which the end of the motor is rotatably mounted to the outer housing, the output shaft of the motor is split in its axial direction and the split shaft parts are coupled by a universal joint. The "universal joint" in this invention refers to a joint which does not affect torque transmission even if the positional relation and angle between the two split shaft parts change. With this construction, when the motor and the impact driving part move with respect to each other in the axial direction of the tool bit due to vibration, the impact tool can smoothly transmit torque of the motor to the impact driving part via the gear, while responding to such relative movement.
- According to a further embodiment of the impact tool of the present invention, the impact tool has a dust-proof cover that covers at least the universal joint.
- According to this invention, a technique is provided for improving the effect of reducing vibration of a handle while securing stable movement in an impact tool.
-
-
FIG. 1 is a sectional view showing an entire structure of a hammer drill having a vibration-proof housing structure according to a first embodiment of the present invention. -
FIG. 2 is also a sectional view showing the entire structure of the hammer drill, in the state in which a compression coil spring is deformed. -
FIG. 3 is an enlarged sectional view showing the vibration-proof housing structure of the hammer drill. -
FIG. 4 is a sectional view showing an entire structure of a hammer drill having a vibration-proof housing structure according to a second embodiment of the present invention. -
FIG. 5 is also a sectional view showing the entire structure of the hammer drill, in the state in which a driving motor is rotated (tilted). -
FIG. 6 is a sectional view taken along line A-A inFIG. 4 . -
FIG. 7 is a sectional view taken along line B-B inFIG. 4 . -
FIG. 8 is a sectional view taken along line C-C inFIG. 4 . -
FIG. 9 is a sectional view taken along line D-D inFIG. 4 . -
FIG. 10 is a sectional view taken along line E-E inFIG. 4 . - A first embodiment of the present invention is now described with reference to
FIGS. 1 to 3 . In this embodiment, an electric hammer drill is explained as a representative example of the impact tool. As shown inFIGS. 1 and2 , thehammer drill 101 according to this embodiment mainly includes anouter housing 103 that forms an outer shell of thehammer drill 101, ahammer bit 119 detachably coupled to a front end region (on the left as viewed inFIG. 1 ) of theouter housing 103 via atool holder 137, and ahandgrip 109 designed to be held by a user and connected to theouter housing 103 on the side opposite to thehammer bit 119. Thehammer bit 119 is held by thehollow tool holder 137 such that it is allowed to linearly move with respect to the tool holder in its axial direction. Theouter housing 103, thehammer bit 119 and thehandgrip 109 are features that correspond to the "outer housing", the "tool bit" and the "handle", respectively, according to the present invention. In this embodiment, for the sake of convenience of explanation, the side of thehammer bit 119 is taken as the front and the side of thehandgrip 109 as the rear. - The
outer housing 103 houses a drivingmotor 111, acrank housing 105 including abarrel 106 and agear housing 107. Thecrank housing 105 including thebarrel 106 and thegear housing 107 form aninner housing 103. Thecrank housing 105 houses amotion converting mechanism 113 and astriking mechanism 115 which move thehammer bit 119 linearly in an axial direction of the hammer bit. Thegear housing 107 houses apower transmitting mechanism 117 which rotates thehammer bit 119 around its axis. Themotion converting mechanism 113, thestriking mechanism 115 and thepower transmitting mechanism 117 form an internal actuating mechanism for driving thehammer bit 119. Thedriving motor 111 is fixed in a lower region of theouter housing 103 such that its rotation axis runs in a vertical direction (vertically as viewed inFIG. 1 ) substantially perpendicular to a longitudinal direction of the outer housing 103 (the axial direction of the hammer bit 119). Thehandgrip 109 is integrally formed with theouter housing 103, so that thedriving motor 111 is substantially integrated with thehandgrip 109. - The
power transmitting mechanism 117 appropriately reduces the speed of torque of thedriving motor 111 and transmits it to themotion converting mechanism 113, and themotion converting mechanism 113 appropriately converts torque of thedriving motor 111 into linear motion and then transmits it to thestriking mechanism 115. Then, an impact force is generated in the axial direction of the hammer bit 119 (the horizontal direction as viewed inFIG. 1 ) via thestriking mechanism 115. Themotion converting mechanism 113 is a feature that corresponds to the "impact driving part" according to this invention. Further, the speed of torque of thedriving motor 111 is appropriately reduced by thepower transmitting mechanism 117 and transmitted to thehammer bit 119 via acylinder 131 and thetool holder 137, so that thehammer bit 119 is caused to rotate in its circumferential direction. The drivingmotor 111 is driven when a user depresses atrigger 109a disposed on thehandgrip 109. - As shown in
FIG. 3 , themotion converting mechanism 113 mainly includes acrank shaft 121 that is rotationally driven in a horizontal plane via thepower transmitting mechanism 117 for transmitting torque of the drivingmotor 111, a crankplate 123 that is caused to rotate together with thecrank shaft 121, acrank arm 127 that is loosely connected to the crankplate 123 via aneccentric shaft 125, and a driving element in the form of a piston 129 which is mounted to thecrank arm 127 via a connectingshaft 128. The piston 129 is slidably disposed within thecylinder 131. When the drivingmotor 111 is driven, the piston 129 is caused to linearly move in the axial direction of thehammer bit 119 within thecylinder 131. - The
striking mechanism 115 mainly includes a striking element in the form of astriker 133 slidably disposed within the bore of thecylinder 131, and an intermediate element in the form of animpact bolt 135 that is slidably disposed within thetool holder 137 and serves to transmit kinetic energy of thestriker 133 to thehammer bit 119. An air chamber 131a is formed between the piston 129 and thestriker 133 in thecylinder 131. Thestriker 133 is driven via pressure fluctuations (air spring action) of the air chamber 131a by sliding movement of the piston 129. Thestriker 133 then collides with (strikes) theimpact bolt 135 which is slidably disposed in thetool holder 137. As a result, a striking force caused by the collision is transmitted to thehammer bit 119 via theimpact bolt 135. - The
power transmitting mechanism 117 mainly includes adriving gear 141, atorque limiter 143, anintermediate shaft 145, afirst bevel gear 147, asecond bevel gear 149, arotary sleeve 151, athird bevel gear 153 and afourth bevel gear 155. Thefirst bevel gear 147, thesecond bevel gear 149, therotary sleeve 151, thethird bevel gear 153 and thefourth bevel gear 155 of thepower transmitting mechanism 117 are housed within thecrank housing 105, and the other members of thepower transmitting mechanism 117 are housed within thegear housing 107. - Torque of the driving
motor 111 is transmitted from thedriving gear 141 formed on theoutput shaft 112 of the drivingmotor 111 to theintermediate shaft 145 via thetorque limiter 143. Thetorque limiter 143 is provided on theintermediate shaft 145 as a safety device which interrupts power transmission from thedriving gear 141 to theintermediate shaft 145 when an excessive load exceeding a set value predetermined by a spring 143a of thetorque limiter 143 is exerted on thehammer bit 119. The torque transmitted to theintermediate shaft 145 is then transmitted from thefirst bevel gear 147 that rotates together with theintermediate shaft 145 in a horizontal plane, to thesecond bevel gear 149 that rotates in a vertical plane in engagement with thefirst bevel gear 147, and then further transmitted from thesecond bevel gear 149 to therotary sleeve 151. - The
rotary sleeve 151 is a cylindrical member which is coaxially disposed on the outside of thecylinder 131 and can move in the longitudinal direction with respect to thecylinder 131, thesecond bevel gear 149 that is disposed on the outside of a front end portion of therotary sleeve 151, and thethird bevel gear 153 that is disposed on the outside of a rear end portion oftherotary sleeve 151. Therotary sleeve 151 is splined to thesecond bevel gear 149 on its front end portion in the longitudinal direction, and also splined to thethird bevel gear 153 on its rear end portion in the longitudinal direction. Therefore, when the drivingmotor 111 is driven, the three members, or thesecond bevel gear 149, therotary sleeve 151 and thethird bevel gear 153 are always caused to rotate together. - The
third bevel gear 153 is engaged with thefourth bevel gear 155 fixed on thecrank shaft 121. Therefore, torque of therotary sleeve 151 is transmitted from thethird bevel gear 153 that rotates in a vertical plane together with therotary sleeve 151, to the crankshaft 121 via thefourth bevel gear 155, so that thecrank shaft 121 rotates in a horizontal plane. Thus, themotion converting mechanism 113 and thestriking mechanism 115 are driven. Therotary sleeve 151 and thefourth bevel gear 155 are features that correspond to the "torque transmitting member" and the "gear", respectively, according to this invention. Thethird bevel gear 153 is rotatably supported by a slidingbearing 169 which is housed within abearing cover 163, and thecrank shaft 121 is rotatably supported by a rolling bearing 167 which is housed within thebearing cover 163. - Further,
clutch teeth 151 a are formed on the inner circumferential surface of therotary sleeve 151 and engage withclutch teeth 131b formed on the outer circumferential surface of thecylinder 131. Therefore, torque of therotary sleeve 151 is transmitted to thecylinder 131 via theclutch teeth hammer bit 119 via thetool holder 137 which is connected to thecylinder 131 by a connectingpin 132, so that thehammer bit 119 is caused to rotate. - An operation mode switching member in the form of an operation
mode switching dial 175 is disposed in an upper surface region of thecrank housing 105 and can be manually operated by a user. The operationmode switching dial 175 can be switched between hammer mode in which thehammer bit 119 is caused to perform at least a hammering operation only by striking movement and hammer drill mode in which thehammer bit 119 is caused to perform a hammer drill operation by striking movement and rotation. By switching the operationmode switching dial 175, therotary sleeve 151 is slid in the axial direction of thehammer bit 119. The operationmode switching dial 175 is mounted to be rotatable around a vertical axis transverse to the axis of thehammer bit 119. The operationmode switching dial 175 has an eccentric shaft part 175a which is engaged with a circumferentially extendingring groove 151b formed in the outer surface of therotary sleeve 151. When the user turns the operationmode switching dial 175, therotary sleeve 151 is slid along thecylinder 131 in the axial direction of thehammer bit 119 via the eccentric shaft part 175a. - When the operation
mode switching dial 175 is switched to hammer drill mode, therotary sleeve 151 is slid rearward (toward the handgrip 109) and theclutch teeth 151a of therotary sleeve 151 engage with theclutch teeth 131b ofthecylinder 131 so that the torque is transmitted to thecylinder 131. Therefore, in this case, themotion converting mechanism 113 and thestriking mechanism 115 are driven, and the torque of therotary sleeve 151 is transmitted to thecylinder 131 and then transmitted to thehammer bit 119 via thetool holder 137 which is connected to thecylinder 131 by the connectingpin 132. Thus, thehammer bit 119 is caused to perform striking movement and rotation. - When the operation
mode switching dial 175 is switched to hammer mode, therotary sleeve 151 is slid forward (toward the hammer bit 119) and theclutch teeth 151a of therotary sleeve 151 are disengaged from theclutch teeth 131b of thecylinder 131 so that the torque is no longer transmitted to thecylinder 131. Therefore, in this case, thehammer bit 119 is caused to perform only striking movement via themotion converting mechanism 113 and thestriking mechanism 115. Thus, therotary sleeve 151 according to this embodiment not only serves to transmit (distribute) the torque of the drivingmotor 111 as a rotational driving power to each of themotion converting mechanism 113 and thehammer bit 119, but also serves as a clutch member for switching the operation mode. - The
tool holder 137 disposed in a front region of thecrank housing 105 is mounted such that it can move in the axial direction of thehammer bit 119 and rotate in the circumferential direction with respect to the crankhousing 105 via afront sliding bearing 161. Thebearing cover 163 disposed in a rear region of thecrank housing 105 is mounted such that it can move in the axial direction with respect to the crankhousing 105 via arear sliding bearing 165. A rear end surface of thebearing cover 163 in the axial direction of the hammer bit is elastically connected to a front surface of a rear end part of thecrank housing 105 via acompression coil spring 171 which contracts and extends in the axial direction of the hammer bit. Thecompression coil spring 171 is a feature that corresponds to the "elastic element" according to this invention. Thecompression coil spring 171 applies a biasing force in such a manner as to push thebearing cover 163 forward. This biasing force is received by arubber ring 173 which is disposed between a rear end flange 137a of thetool holder 137 and an inner stepped part 106a of thebarrel 106. - Specifically, in this embodiment, not only the
tool holder 137, thecylinder 131, themotion converting mechanism 113 and thestriking mechanism 115, but the third andfourth bevel gears power transmitting mechanism 117 which are supported by thebearing cover 163 are connected to the crankhousing 105 such that they can move in the axial direction of thehammer bit 119 via thecompression coil spring 171. The crankhousing 105 is integrated with theouter housing 103. Therefore, theouter housing 103 integrally formed with thehandgrip 109 is elastically connected via thecompression coil spring 171 to themotion converting mechanism 113 and the striking mechanism 115 (which may also be hereinafter referred to as a striking mechanism part including both of themotion converting mechanism 113 and the striking mechanism 115) which are sources of vibration. - In the
hammer drill 101 constructed as described above, when the user holds thehandgrip 109 and depresses thetrigger 109a in order to drive the drivingmotor 111, while applying a pressing force to theouter housing 103 in the axial direction of thehammer bit 119 and pressing thehammer bit 119 against the workpiece, the torque of the drivingmotor 111 is transmitted from therotary sleeve 151 of thepower transmitting mechanism 117 to themotion converting mechanism 113 via the third andfourth bevel gears cylinder 131 via themotion converting mechanism 113. By this sliding movement, thestriker 133 is caused to linearly move within thecylinder 131 via air pressure fluctuations or air spring action in the air chamber 131a of thecylinder 131. Thestriker 133 then collides with theimpact bolt 135, so that the kinetic energy caused by this collision is transmitted to thehammer bit 119. - At this time, when the operation
mode switching dial 175 is placed in the hammer mode, therotary sleeve 151 is slid forward and theclutch teeth 151 a of therotary sleeve 151 are disengaged from theclutch teeth 131b of thecylinder 131 so that the torque is no longer transmitted to thecylinder 131. Therefore, thehammer bit 119 performs a hammering operation only by striking movement in its axial direction. - On the other hand, when the operation
mode switching dial 175 is placed in the hammer drill mode, therotary sleeve 151 is slid rearward and theclutch teeth 151a of therotary sleeve 151 are engaged with theclutch teeth 131b of thecylinder 131 so that the torque of the drivingmotor 111 is transmitted to thecylinder 131 via therotary sleeve 151. Therefore, thecylinder 131 and thetool holder 137 are rotationally driven in a vertical plane and thehammer bit 119 is caused to rotate together with thetool holder 137. Thus, thehammer bit 119 performs a hammer drill operation (drilling operation) on a workpiece (concrete) by striking movement in the axial direction and rotation in the circumferential direction. - During hammering or hammer drill operation, impulsive and cyclic vibration is caused in the striking mechanism part (the
motion converting mechanism 113 and the striking mechanism 115) in the axial direction of thehammer bit 119. By this vibration, thecompression coil spring 171 elastically deforms, so that themotion converting mechanism 113 connected via thecompression coil spring 171 is caused to move in the axial direction of thehammer bit 119 with respect to the crankhousing 105. Thus, transmission of vibration from themotion converting mechanism 113 to the crankhousing 105 can be reduced.FIG. 2 shows the state in which thecompression coil spring 171 is deformed. Thus, theouter housing 103 to which thecrank housing 105 is fixed, and thehandgrip 109 which is integrally formed with theouter housing 103 are vibration-proofed. - In this case, in this embodiment, the driving
motor 111 is fixed to theouter housing 103. With such a construction in which the drivingmotor 111 as a mass is fixed to theouter housing 103, the mass of thehandgrip 109 which is integrated with theouter housing 103 can be made relatively large with respect to themotion converting mechanism 113 and thestriking mechanism 115 which causes thehammer bit 119 to perform striking movement, so that the effect of vibration-proofing thehandgrip 109 can be enhanced. - Further, in this embodiment, not only the driving
motor 111, but the inner housing including thecrank housing 105 and thegear housing 107 and most of the components or elements of thepower transmitting mechanism 117 housed within thecrank housing 105 and thegear housing 107 are fixed or disposed on theouter housing 103 side. Therefore, the mass of theouter housing 103 side is further increased by these members as well as the drivingmotor 111, so that the effect of vibration-proofing thehandgrip 109 can be further enhanced. - Further, in this embodiment, the
rotary sleeve 151 is connected such that it can move in the axial direction with respect to thecylinder 131 and thethird bevel gear 153 and rotate together with thecylinder 131 and thethird bevel gear 153. Therefore, therotary sleeve 151 can transmit torque of thesecond bevel gear 149 to thecylinder 131 and thethird bevel gear 153 without being affected by vibration caused in the axial direction of the hammer bit. - Further, in this embodiment, the torque of the driving
motor 111 is distributed by therotary sleeve 151 to a path for striking power of striking thehammer bit 119 and a path for rotating power of rotating thehammer bit 119. Therefore, components relating to power transmission between therotary sleeve 151 and thedriving gear 141, including therotary sleeve 151, are used in common to the both paths. Thus, the number of parts for driving thehammer bit 119 can be rationally reduced. - Further, in this embodiment, in order to drive the
motion converting mechanism 113, the third andfourth bevel gears bearings 167, 169 in thebearing cover 163 are connected such that they can move together with themotion converting mechanism 113 in the axial direction of the hammer bit with respect to theouter housing 103. Therefore, the positional relation between themotion converting mechanism 113 and the third andfourth bevel gears - Hammering or hammer drill operation by the hammer bit is performed while the user holding the
handgrip 109 applies a pressing force to theouter housing 103 in the axial direction of thehammer bit 119 and presses thehammer bit 119 against the workpiece. In this embodiment, thetool holder 137 and thebearing cover 163 are supported via the front and rear slidingbearings housing 105, or specifically they are allowed to move only in the axial direction with respect to the crankhousing 105. With this construction, thehammer bit 119 can be pressed against the workpiece in stable condition. - A
hammer drill 201 according to a second embodiment of the present invention is now described with reference toFIGS. 4 to 10 . An internal actuating mechanism for driving a hammer bit 219 (amotion converting mechanism 213 for causing thehammer bit 219 to perform striking movement and a striking mechanism (not shown)) and apower transmitting mechanism 217 for transmitting torque to thehammer bit 219 have substantially the same construction as those of the above-described first embodiment. In this embodiment, however, for the sake of convenience of explanation, part of themotion converting mechanism 213 is shown inFIG. 8 , and part of thepower transmitting mechanism 217 is shown inFIG. 7 . Themotion converting mechanism 213 is a feature that corresponds to the "impact driving part" according to this invention. - As shown in
FIGS. 4 and5 , anouter housing 203 is integrally formed with ahandgrip 209. Theouter housing 203 and thehandgrip 209 are features that correspond to the "outer housing" and the "handle", respectively, according to the present invention. As shown inFIGS. 4 to 6 , theouter housing 203 houses amotor housing 208 which houses a drivingmotor 211, and aninner housing 205 which houses themotion converting mechanism 213, the striking mechanism and thepower transmitting mechanism 217. The drivingmotor 211 is driven when a user depresses a trigger 209a disposed on thehandgrip 209. The drivingmotor 211 is disposed such that its rotation axis runs in a vertical direction (vertically as viewed inFIG. 4 ) substantially perpendicular to the axial direction of thehammer bit 219, and at an end (lower end) of the driving motor which faces away from the axis of thehammer bit 219, themotor housing 208 is mounted to theouter housing 203 such that it can rotate on ashaft 281 in the axial direction of the hammer bit. - One (rear) end of the
inner housing 205 in the axial direction is connected to theouter housing 203 via ball-like vibration-proofingelastic rubbers 283, 284 (two each on its upper and lower ends in this embodiment) such that it can move in the axial direction of thehammer bit 219 with respect to theouter housing 203. The other end of theinner housing 205 in the axial direction is supported via arubber ring 285 having a circular section with respect to theouter housing 203 such that it can move in the axial direction of thehammer bit 219 with respect to theouter housing 203. Specifically, in this embodiment, theinner housing 205 which houses themotion converting mechanism 213 and the striking mechanism which are sources of vibration and thepower transmitting mechanism 217 is connected to theouter housing 203 which is integrally formed with thehandgrip 209, via theelastic rubbers outer housing 203. Theelastic rubbers -
FIG. 9 shows the upper twoelastic rubbers 283, andFIG. 10 shows the lower twoelastic rubbers 284. As shown in the drawings, the upper and lowerelastic rubbers hammer bit 219. The upper and lowerelastic rubbers concave surface 286a of anouter rubber support 286 formed on theouter housing 203 and a generally semispherical concave surface 287a of aninner rubber support 287 formed on theinner housing 205. - In this embodiment, in the connecting structure of the outer and
inner housings elastic rubbers handgrip 209 side, and as for the lower right and left parts, the mating surfaces of the outer and inner rubber supports 286, 287 which face each other are formed in a generally V configuration as viewed from thehandgrip 209 side. Specifically, the mating surfaces of the outer and inner rubber supports 286, 287 which face each other are parallel in the axial direction of thehammer bit 119 and inclined at an angle of about 45 degrees in the horizontal direction and the vertical direction transverse to the axial direction. With this construction, in the axial direction, a force in a shearing direction mainly acts upon theelastic rubbers - The
rubber ring 285 is provided as a guide member for guiding movement of theinner housing 205 with respect to theouter housing 203 in the axial direction of the hammer bit. Therubber ring 285 is disposed in a ring-shaped space which is defined between an outer surface oftheinner housing 205 and a front surface of a ring-shapedouter flange 205a formed on the outer surface of theinner housing 205, and an inner surface of theouter housing 203 and a ring-shaped inner flange 203a formed on the inner surface of theouter housing 203. Thus, therubber ring 285 prevents theinner housing 205 from uselessly moving in a direction transverse to the axial direction of the hammer bit with respect to theouter housing 103. Therefore, when performing a hammering or hammer drill operation while pressing thehammer bit 219 against a workpiece, thehammer bit 219 can be prevented from uselessly moving in a direction transverse to the axial direction of the hammer bit with respect to theouter housing 103, so that operation can be performed in stable condition. - As shown in
FIG. 6 , anoutput shaft 212 of the drivingmotor 211 extends into theinner housing 205 and adriving gear 241 is formed on the extending end of theoutput shaft 212, so that themotion converting mechanism 213 is driven by a drivengear 242 which is engaged with thedriving gear 241. The drivengear 242 is a feature that corresponds to the "gear" according to this invention. InFIG. 8 , acrank shaft 221 to which the drivengear 242 is fixed, a crankplate 223, aneccentric shaft 225 and acrank arm 227 of themotion converting mechanism 213 are shown. - In
FIG. 7 , atorque limiter 243, anintermediate shaft 245 and afirst bevel gear 247 of thepower transmitting mechanism 217 are shown. In this embodiment, thetorque limiter 243 is driven by the drivengear 242, and torque is transmitted from thefirst bevel gear 247 to a tool holder (not shown) directly or via a second bevel gear (not shown) and a cylinder (not shown). - The
motor housing 208 which houses the drivingmotor 211 rotates on theshaft 281 in the axial direction of the hammer bit when the inner andouter housings output shaft 212 of the drivingmotor 211 is split in its axial direction into a body-side shaft part 212a and a tip-side shaft part 212b on which thedriving gear 241 is formed. An axially extendinghexagonal hole 291 is formed in an end portion of the body-side shaft part 212a, and aspherical element 292 having a hexagonal section is formed on the tip-side shaft part 212b. Thespherical element 292 is fitted in thehexagonal hole 291 such that it can move in the extending direction of the hole (in the axial direction of the shaft) with respect to the hole. Thus, the body-side shaft part 212a and the tip-side shaft part 212b are connected such that torque can be transmitted therebetween and can flex at the joint. Thehexagonal hole 291 and thespherical element 292 form the "universal joint" according to this invention. Further, axial ends of the tip-side shaft part 212b are rotatably supported by theinner housing 205 via bearings. - Further, the body-side shaft part 212a is supported by the
inner housing 205 via aspherical bearing 295 such that it can move in all directions with respect to the inner housing. Thespherical bearing 295 includes a sphericalconcave part 293 which is mounted to theinner housing 205, and aspherical element 294 which is fitted in the sphericalconcave part 293. Thespherical element 294 is mounted on an outer surface of an end portion of the body-side shaft part 212a such that it can slide in the axial direction of the shaft. InFIG. 5 , theinner housing 205 is shown moved rearward (toward the handgrip 209) in the axial direction of the hammer bit with respect to theouter housing 203, so that the drivingmotor 211 rotates rearward and theoutput shaft 212 flexes into a generally dogleg form. - Further, a flexible (rubber) dust-
proof cover 297 covers regions of themotor housing 208 and theinner housing 205 which include a joint between the body-side shaft part 212a and the tip-side shaft part 212b. - The
hammer drill 201 according to this embodiment is constructed as described above. Therefore, during operation, impulsive and cyclic vibration is caused in theinner housing 205 in the axial direction of thehammer bit 219 by driving of the striking mechanism part. However, transmission of vibration from theinner housing 205 to theouter housing 203 and thehandgrip 209 side is reduced by elastic deformation of theelastic rubbers motor 211 is mounted to theouter housing 203 such that it can rotate in the axial direction of the hammer bit. With such a construction in which the drivingmotor 211 as a mass is mounted to theouter housing 203, the mass of thehandgrip 209 which is integrated with theouter housing 203 can be made relatively large with respect to theinner housing 205 which houses the striking mechanism part, so that the effect of vibration-proofing thehandgrip 109 can be enhanced. - Further, the
elastic rubbers elastic rubbers handgrip 209 by shearing deformation of theelastic rubbers - Further, the
elastic rubbers hammer bit 219. With this construction, the outer andinner housings hammer bit 219 can be pressed against the workpiece in stable condition. - Further, in this embodiment, the
driving gear 241 and the drivengear 242 which drive themotion converting mechanism 213 are disposed in theinner housing 205 and connected to theouter housing 203 together with themotion converting mechanism 213 such that they can move in the axial direction of the hammer bit with respect to theouter housing 203. Therefore, the positional relation between themotion converting mechanism 213, thedriving gear 241 and the drivengear 242 is held constant regardless of vibration, so that stable and smooth movement can be ensured. - In the second embodiment, the
elastic rubbers 283 284 are described as being spherical, but they may be cylindrical. Further, the joint structure of thesplit output shaft 212 is described as being constructed such that thehexagonal hole 291 is formed in the body-side shaft part 212a and thespherical element 292 having a hexagonal section is formed in the tip-side shaft part 212b, but they may be formed vice versa. The universal joint is not limited to the structure comprising thehexagonal hole 291 and thespherical element 292 having a hexagonal section.
Further, in the above-described first and second embodiments, a hammer drill is described as a representative example of the impact tool, but the present invention may also be applied to a hammer in which thehammer bit - In view of the above-described invention, the following aspects can be provided. Aspect 1
"The impact tool as defined in any one of claims 1 to 3, comprising an inner housing that houses the impact driving part, wherein the inner housing is fixed to the outer housing." - "The impact tool as defined in aspect 1, wherein the impact driving part is supported via front and rear sliding bearings in the inner housing and can slide in the axial direction of the tool bit with respect to the inner housing."
- "The impact tool as defined in claim 3, further comprising an operation mode switching member that is switched between hammer mode in which the tool bit is caused to perform an operation only by striking movement and hammer drill mode in which the tool bit is caused to perform an operation by striking movement and rotation, wherein the torque transmitting member also serves as a clutch member for switching operation mode which transmits torque of the motor to the tool bit when the operation mode switching member is switched to hammer drill mode, and interrupts the torque transmission when the operation mode switching member is switched to hammer mode."
- "The impact tool as defined in any one of claims 1 to 6, comprising a motion converting mechanism that converts torque into linear motion, and a striking element that is linearly driven by the motion converting mechanism and applies a striking force to the tool bit."
- "The impact tool as defined in any one of claims 4 to 6, wherein the elastic element comprises an elastic rubber, and the elastic element mainly undergoes shearing deformation in the axial direction of the hammer bit and mainly undergoes compressive deformation in a direction transverse to the axial direction of the hammer bit."
- "The impact tool as defined in claim 6, wherein the universal joint for coupling the split shaft parts comprises a hexagonal hole formed in one of the split shaft parts and a spherical element having a hexagonal section which is formed on the other split shaft part and fitted in the hexagonal hole."
-
- 101
- hammer drill (impact tool)
- 103
- outer housing
- 105
- crank housing
- 106
- barrel
- 106a
- inner stepped portion
- 107
- gear housing
- 109
- handgrip (handle)
- 109a
- trigger
- 111
- driving motor (motor)
- 112
- output shaft
- 113
- motion converting mechanism (impact driving part)
- 115
- striking mechanism
- 117
- power transmitting mechanism
- 119
- hammer bit (tool bit)
- 121
- crank shaft
- 123
- crank plate
- 125
- eccentric shaft
- 127
- crank arm
- 128
- connecting shaft
- 129
- piston
- 131
- cylinder
- 131a
- air chamber
- 131b
- clutch teeth
- 132
- connecting pin
- 133
- striker
- 135
- impact bolt
- 137
- tool holder
- 137a
- rear end flange
- 141
- driving gear
- 143
- torque limiter
- 143a
- spring
- 145
- intermediate shaft
- 147
- first bevel gear
- 149
- second bevel gear (bit driving gear)
- 151
- rotary sleeve (rotation power transmitting member)
- 151a
- clutch teeth
- 151b
- ring groove
- 153
- third bevel gear (power transmitting gear)
- 155
- fourth bevel gear (gear)
- 161
- front sliding bearing
- 163
- bearing cover
- 165
- rear sliding bearing
- 167
- rolling bearing
- 169
- sliding bearing
- 171
- compression coil spring (elastic element)
- 173
- rubber ring
- 175
- operation mode switching dial (operation mode switching member)
- 175a
- eccentric shaft part
- 201
- hammer drill (impact tool)
- 203
- outer housing
- 203 a
- inner flange
- 205
- inner housing
- 205a
- outer flange
- 208
- motor housing
- 209
- handgrip (handle)
- 209a
- trigger
- 211
- driving motor (motor)
- 212
- output shaft
- 212a
- body-side shaft part
- 212b
- tip-side shaft part
- 213
- motion converting mechanism (impact driving part)
- 217
- power transmitting mechanism
- 219
- hammer bit (tool bit)
- 221
- crank shaft
- 223
- crank plate
- 225
- eccentric shaft
- 227
- crank arm
- 241
- driving gear
- 242
- driven gear (gear)
- 243
- torque limiter
- 245
- intermediate shaft
- 247
- first bevel gear
- 281
- shaft
- 283, 284
- elastic rubber (elastic element)
- 285
- rubber ring
- 286
- outer rubber support
- 286a
- spherical concave surface
- 287
- inner rubber support
- 287a
- spherical concave surface
- 291
- hexagonal hole
- 292
- spherical element
- 293
- spherical concave part
- 294
- spherical element
- 295
- spherical bearing
- 297
- dust-proof cover
Claims (7)
- An impact tool that linearly move a tool bit in an axial direction of the tool bit to perform a predetermined operation, comprising:a handle to be held by a user,an outer housing that is integrally formed with the handle,a motor that is disposed in an outer housing such that its rotation axis runs transversely to the axial direction of the tool bit,a gear that is rotationally driven by receiving torque of the motor in the outer housing,an impact driving part that is driven by the gear in the outer housing, anda striking element that is driven by the impact driving part and linearly moves the tool bit,characterized in that the motor is mounted to the outer housing, and the outer housing is connected to the impact driving part and the gear via an elastic element and can move in the axial direction of the tool bit with respect to the impact driving part and the gear.
- The impact tool as defined in claim 1, wherein the motor is fixed to the outer housing and integrated with the handle.
- The impact tool as defined in claim 1 or 2, comprising a torque transmitting member that is disposed on the outer housing side and rotates around an axis of the tool bit by receiving torque of the motor, and a power transmitting gear that rotates together with the torque transmitting member and transmits the torque to the gear, wherein the power transmitting gear can move together with the impact driving part in the axial direction of the tool bit with respect to the torque transmitting member while being held in engagement with the gear.
- The impact tool as defined in claim 3, further comprising a bit driving gear that causes the tool bit to rotate in a circumferential direction by receiving the torque of the motor, wherein the power transmitting gear is rotationally driven by the bit driving gear via the torque transmitting member.
- The impact tool as defined in claim 1, wherein an end of the motor which faces away from an axis of the tool bit in a direction of a rotation axis of the motor is mounted to the outer housing such that the motor can rotate in the axial direction of the tool bit.
- The impact tool as defined in claim 5, wherein the output shaft of the motor is split in its axial direction and the split shaft parts are coupled by a universal joint.
- The impact tool as defined in claim 6, comprising a dust-proof cover that covers at least the universal joint.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2009089252A JP5356097B2 (en) | 2009-04-01 | 2009-04-01 | Impact tool |
PCT/JP2010/055923 WO2010114055A1 (en) | 2009-04-01 | 2010-03-31 | Impact tool |
Publications (4)
Publication Number | Publication Date |
---|---|
EP2415563A1 true EP2415563A1 (en) | 2012-02-08 |
EP2415563A4 EP2415563A4 (en) | 2014-04-09 |
EP2415563B1 EP2415563B1 (en) | 2015-08-12 |
EP2415563B9 EP2415563B9 (en) | 2015-11-04 |
Family
ID=42828344
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10758826.1A Active EP2415563B9 (en) | 2009-04-01 | 2010-03-31 | Impact tool |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2415563B9 (en) |
JP (1) | JP5356097B2 (en) |
RU (1) | RU2531221C2 (en) |
WO (1) | WO2010114055A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2468455A1 (en) * | 2009-12-25 | 2012-06-27 | Makita Corporation | Striking tool |
CN106457544A (en) * | 2014-06-12 | 2017-02-22 | 株式会社牧田 | Impact tool |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6022318B2 (en) * | 2012-11-19 | 2016-11-09 | 株式会社マキタ | Hammer drill |
CN109555792B (en) * | 2018-12-05 | 2023-10-13 | 浙江亚特电器股份有限公司 | Electric hammer clutch device |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2154497A (en) * | 1984-02-18 | 1985-09-11 | Bosch Gmbh Robert | Hand machine tool, particularly hammer drill or percussion drill |
US5678641A (en) * | 1994-05-02 | 1997-10-21 | Hilti Aktiengeschaft | Drilling and chipping tool |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10130088C2 (en) | 2001-06-21 | 2003-10-16 | Hilti Ag | Striking electric hand tool device with active vibration damping |
ATE396841T1 (en) * | 2004-12-23 | 2008-06-15 | Black & Decker Inc | POWER TOOL HOUSING |
ATE396838T1 (en) * | 2004-12-23 | 2008-06-15 | Black & Decker Inc | POWER TOOL HOUSING |
US7383895B2 (en) * | 2005-08-19 | 2008-06-10 | Makita Corporation | Impact power tool |
DE102005059180A1 (en) * | 2005-12-12 | 2007-06-14 | Robert Bosch Gmbh | Hand tool with a drive train and a decoupling unit |
-
2009
- 2009-04-01 JP JP2009089252A patent/JP5356097B2/en active Active
-
2010
- 2010-03-31 EP EP10758826.1A patent/EP2415563B9/en active Active
- 2010-03-31 WO PCT/JP2010/055923 patent/WO2010114055A1/en active Application Filing
- 2010-03-31 RU RU2011144111/02A patent/RU2531221C2/en active
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2154497A (en) * | 1984-02-18 | 1985-09-11 | Bosch Gmbh Robert | Hand machine tool, particularly hammer drill or percussion drill |
US5678641A (en) * | 1994-05-02 | 1997-10-21 | Hilti Aktiengeschaft | Drilling and chipping tool |
Non-Patent Citations (1)
Title |
---|
See also references of WO2010114055A1 * |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2468455A1 (en) * | 2009-12-25 | 2012-06-27 | Makita Corporation | Striking tool |
EP2468455A4 (en) * | 2009-12-25 | 2014-02-26 | Makita Corp | Striking tool |
US9999967B2 (en) | 2009-12-25 | 2018-06-19 | Makita Corporation | Striking tool |
CN106457544A (en) * | 2014-06-12 | 2017-02-22 | 株式会社牧田 | Impact tool |
US20170106517A1 (en) * | 2014-06-12 | 2017-04-20 | Makita Corporation | Impact tool |
EP3156185A4 (en) * | 2014-06-12 | 2018-01-17 | Makita Corporation | Impact tool |
CN106457544B (en) * | 2014-06-12 | 2019-05-31 | 株式会社牧田 | Percussion tool |
Also Published As
Publication number | Publication date |
---|---|
WO2010114055A1 (en) | 2010-10-07 |
EP2415563B9 (en) | 2015-11-04 |
RU2531221C2 (en) | 2014-10-20 |
JP5356097B2 (en) | 2013-12-04 |
RU2011144111A (en) | 2013-05-10 |
JP2010240756A (en) | 2010-10-28 |
EP2415563A4 (en) | 2014-04-09 |
EP2415563B1 (en) | 2015-08-12 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US8695724B2 (en) | Hand-held power tool | |
EP2018939B1 (en) | Power tool with vibration damping mechanism | |
EP2418051B1 (en) | Impact tool | |
EP2808130B1 (en) | Reciprocating power tool | |
EP2384860B1 (en) | Power tool housing | |
US7059425B2 (en) | Reciprocating power tool | |
EP1741520B1 (en) | Motor support structure of a power tool | |
RU2606140C2 (en) | Impact tool | |
US9724814B2 (en) | Impact tool | |
US9085075B2 (en) | Power tool | |
JP2009509790A (en) | Electric machine tool | |
US10500706B2 (en) | Power tool | |
US8720599B2 (en) | Power tool with rotatable tool holder | |
EP2415563B1 (en) | Impact tool | |
JP2008307655A (en) | Impact tool | |
JP2017042888A (en) | Impact tool | |
JP2013163234A (en) | Impact tool |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20111011 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR |
|
DAX | Request for extension of the european patent (deleted) | ||
A4 | Supplementary search report drawn up and despatched |
Effective date: 20140307 |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: B25D 16/00 20060101ALI20140304BHEP Ipc: B25D 17/00 20060101ALI20140304BHEP Ipc: B25D 17/24 20060101AFI20140304BHEP |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: B25D 17/24 20060101AFI20150225BHEP Ipc: B25D 16/00 20060101ALI20150225BHEP Ipc: B25D 17/00 20060101ALI20150225BHEP |
|
INTG | Intention to grant announced |
Effective date: 20150319 |
|
RIN1 | Information on inventor provided before grant (corrected) |
Inventor name: TAKEUCHI, HAJIME Inventor name: KASUYA, YOSHIHIRO Inventor name: FURUSAWA, MASANORI |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 741713 Country of ref document: AT Kind code of ref document: T Effective date: 20150815 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602010026637 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MK05 Ref document number: 741713 Country of ref document: AT Kind code of ref document: T Effective date: 20150812 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20150812 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151113 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151112 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 Ref country code: AT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151214 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151212 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 7 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602010026637 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20160513 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160331 Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 Ref country code: LU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160331 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160331 Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160331 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160331 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 8 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 9 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20100331 Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150812 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20230208 Year of fee payment: 14 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20230209 Year of fee payment: 14 Ref country code: DE Payment date: 20230131 Year of fee payment: 14 |